Fitting of members



o. L. STARR 4 FITTING 0F MEMBERS May 30, 1944.,

Fil'ed Ju1y8, 1940 5 Sheets-Shee'c l INVENTOR.

V 9^ I v7/ N `2 'Nfm 05ml? L. fme' wf,

ATTORNEY.

May so, 1944. Q. L. STARR 2,349,919

l llllll ya' I/ W/ X si tv INVENTOR.- OJC/iE L. 5TH/EE BY Y 4 M /f 27h ATTORNEY.

May 30, 1944- l o. L. STARR I l 2,349,919 l I FI 0F MEMBERS Filed July s.' 1940 s sheets-sheet s il INVENTOR.

05m/@ANMB BY M 77,

` ATTORNEY.

in an axial or longitudinal Patented Mayan, i944 f UNITED STATES PArEN'T FFICE .rrrrmc orrmmnas omnsummnsanrm,

l tocate'rpillarhaetorco.,8anlieandro Calif aoorporationotcalifornia Calif., assigner Appunti@ my s, 1ste, serial No. rusos 11 ici. sca-za) Myinvention relates to control .of the iit bel tween members under-.varying temperature conband in which afpiston ring is adapted to be seated in a groove formed in the band instead of in the body of the piston. As is explained more fully in the speciiication of such application, the piston body is of a relatively soft metal, such as aluminum, which is advantageous because of lightness and high heat conductivity; and the band is of harder metal, such as cast iron, to provide a wear resistant seat for a piston ring seated in the ring groove, so as to preclude wear between the piston ring and its seating groove, and thereby enhance maintenance of proper sealing relationship of the piston ring in such groove and with a cylinder wall. Also, the band. being free of molecular union with the body of the piston, has a limited degree of freedom of move-y ment which is desirable because then the piston ring mounted thereon will not follow all distortions ofthe piston resulting from temperature variations. Such band' although it seats inthe piston with slight radial or transverseclearance at its inner'side, is held between seating surfaces which extend transversely with respectto the,

piston axis. Thus the band has a fit in the piston direction with reference to the piston axis. In the following descrip'- tion, the terms longitudinal or axial are employed for designating such llt ofthe annular member or band.

Since the ring groove bandv is preferably of cast iron while the body of the piston is preferably of aluminum, the body has a greater coeillcient of expansion. As a result, should the band be seated between parallel seating, surfaces extending transversely with respect to the piston axis, and should it have an axially tight llt when the parts are cold, it becomes loose when the parts are subjected to engineoperating temperatures Hence. the piston ring seated in such axially loose band may not be maintained in proper sealing alinement with respect to the cylinder wall, which would result in loss of sealing 'eiiiciency Also, an axially loose band might permit leakage between it and the piston body, which is obviously undesirable. Such looseness of the band under engine operating temperatures becomes aggravated as the operating life of the piston progresses because of the forces resulting from movement A of the piston in a cylinder. Even if the dimensions of the parts are chosen so that the band will originally have a proper tight axial t between parallel seating surfaces, under engine operation temperatures, it may ilt too tight when cold which might cause distortion of the band with consequent misalinement of the piston ring. Should the band and the body of the piston lbe of thesame material, the band being at the periphery of the piston and consequently in contact with the cylinder wall', might be at a diiferent temperature than the body of the piston under engine operating conditions. Therefore. it would have a diiferent degree of expansion and might become loose which is undesirable for the reason previously explained.

My invention is. designed to overcome the above-described problem and has as its objects, among others, the provision of means for maintaining a predetermined controlled nt between members under varying temperature conditions, and particularly a substantially tight non-distorting lit of an annular member mounted in the periphery of a piston, irrespective ofthe temperature to which such piston may be subjected. Other objects of my invention will become aD- parent from a perusal of the. following description thereof.

In general, my invention takes advantage of the phenomenon that, irrespective of shape.' every body during expansion or contractionthereof. resulting from changes in temperature, will always change its size proportionally with respect toa neutral locus which may be also designated as a reference base unaffected by changes in' temperature. Inthe casel of a sphere, such locus is a point, namely, the center of the sphere; while in the oase of a cylindrically shaped body, such as an internal combustion engine piston, the locus is the axis of the cylinder. The latteris also true with respect to prismatically shaped bodies: and

even with respect to an irregularly shaped body,

.under varying temperature conditions, by seating such member between transversely extending;`

nIiig..5isareduced 'sectional vieyv'of a vpiston at room temperature tion,l a tightnonfdistorting fit will bemaintained atA all titties'irijespectivej'` of temperature"1y conditions, but by locating it so as to have a. predetermined spaced relationshipwith respect'to suc h;,4

locus, theparts may be caused to have a. tight to illustrate how the band may be made to have t when hot and a loose i'lt when cold,-or"vice versa, as will be explained; more fullyN-,hereihi after.

In the preferred form of invention is now employed, the above-describedy 'pistn 'wherein my.

ring band is formed with seating surfaces seated" between complementary seating surfaces in, the periphery of the piston, and which extend transversely with respect to theplston axis and'4 are inclinedy withfrespect to 'each other toI'ma-ke-an angle llliling its apex` substantially on thevaxis of the piston ytoV provide a substantially con-` stantly vtightv non-distorting and unifo'rrnaxial fit irrespective of whetherthe pistonis -hot vor cold.` Thus, the piston ring will always be properlyalined with respect to the'cylinder wall; and be'prope'rly seated in its seating groove 'with the sides thereof parallel to Athe sides of such seating groove.y` As an alternative but not as desirable means for maintaining the substantially tight axial fit,` irrespective of whether-the piston is hot orl cold, such band may be yheld in `position by resilient means thrusting against it.. f'

Av loose axialy ilt may be yprovided between the band andthe remainder of the piston lwhen thev parts are" coldv and a tight axial fit when the parts are hot by rendering the angie of the seating surfaces excessive compared to the sizeof thevangle having its apex substantially on the axis of the'piston, sothat the apex is spaced from theaxis and is atja less distance from the periphery of the piston than the radial distance. On the other hand, a loose'v axialt may provided between the parts when they are hot and a tight.` axial t when cold by rendering 'the' angle insuilicient compared to thesizey of the angle having its apex substantially@ 'the axis of thea loose fit when the piston is at room temperature.

Fig. 6 is an enlarged fragmentary section of the ring groove band and the piston seating portion therefor of the ,piston appearing in'Fig. 5.

Fig. 'l is a view ofthe piston of Fig. 5 expanded by heatrto illustrate how thering ygroove band seats when'lthe piston is substantially atf working temperature; the size of the piston of Fig. '7 being exaggerated. l

Fig. v 8 is a reduced scale fragmentary vertical sectional view of a piston' at room temperature provided .with a s tillfdifierent character oi ring groove bandmounting; the relationship of the -fband `with-respect. to its seating groove being exaggerated, to illustrate how the band may be made to haveatight t when the piston is at room temperature.

Fig. 9 is an enlarged fragmentary section of the ring groove band and the piston seat ing'por` vtion thereforof the piston appearing in'v Fig. 8.'

Fig. 10 is a view'of the piston of1Fig.v8 expanded by heatA to illustrate h w the ring groove t band seats when the piston Is substantially at working temperature; the size of the piston of Fig. 10 being exaggerated.

Fig. l1 isa fragmentary vertical sectional view through a piston and cylinder, illustrating a modified forni of construction. Fig. 12 is a fragmentary vertical sectional view through a'piston and cylinder, illustrating a further modification.

Fig. 13 is an enlarged fragmentaryvertical sec- ,tion of the ring groove band and the piston seating portion therefor of the piston appearing `in Fig. 12.

Although the principle of my invention may be employed in any body having ya band or ring like member mounted in a peripheral portion thereof, I have illustrated it in connection with a preferred V forni of piston, disclosed in my previously mentioned co-pending application, and which is now employed in a compression ignition (Diesellengine manufactured by my assignee.v With reference to Figs. 1 and 2, such pistoncompses aluminum -piston body l adapted to work in cylinder wall 2,

and which is provided with, an offset substanv tiallys'pherical combustion crater 3 in the crown piston; so' that4v the apex is spaced fromthe axis and is ata greater distance from 'the periphery of the piston than the radial distance..

L Reference is now made to the drawings yfor a more 'detailed description of the invention.

Fig. l'is a fragmentary vertical sectional view throughs piston and cylinder1 when the parte are at room temperature, illustratmg the feature of my, invention employed therein; I

Fig. Zis a section taken in aplane indicated thereof; the under wall 4 of such crater being tapered to effect uniform flow of heat tothe peripheral ring belt portion 6 of the piston.` An,

' .annular member in the form of a cast iron one piece or integralunbroken ring groove band. l.

independent of the'body I of the piston, is seated in the periphery of the'piston adjacent itsl crown:

the seating of such band being'in a peripheral groove about piston axis A; one surface 8 'of- A which groove is formed on a shoulder resulting 'relationship of the b'and with respect to its seating groove being exaggerated,v to illustrate how the ring groove band seats when the partsare 'at room temperature.

Fig. 4 isa view ofthe pistonv of Fig. 3 expanded l 'l by heat to illustrate how the :ring groove band seats when `the piston is substantially at working temperature: the size of the piston of Fig. being r exaggerated. I

scale fragmentary vertical providedwith a different character of ringv groove band mmmting; the relationship of the band with .respect to its'seatinggroove being exaggerated,

from the provision of a peripheral recess 9 formed in the .top peripheral portion of the piston. The

opposite surface Il of such peripheral groove for t seatingl band l is formed. on internally threaded securing ring or nut i2 having al screw connec- .l tion in recess 9 with piston body I, and which is. I' preferably of the same material as' thebody cf- Y the piston, namely aluminum, but which may beV of any other suitable material.

By turning securing ring l2 the correct number of turns, the proper degree of pressure may be applied to hold or clamp ring' groove band I firmly in position;l and because o'f such firm hol".- ing of-the band, it cannot lrotate about the axis of th iston. -To prevent rotational movement of securing ring I2 after it is once 'screwed on the piston the proper extent. I'provide'tapered `recess 9 in the'body of the piston, is substantially at a right angle with respect to axis A, the side `determined by seating surface 3 may be also inclined or slanted so as to form an oblique angle with respect to axis A. However, I preferably make lower seating surface 8 and the complementary seating surface on band l, extenduat a right angle with respect to axis A, because such arrangement renders it easier to manufacture a substantially perfect transverse seat between the band and such shoulder, and thus provide for more perfect alinement of ring il with the cylinder wall 2. In this connectionfthe inclination of upper seating surface il, which is on ring I2,

and the inclination of the complementary surface on band T, provide conical surfaces which when engaged by securing of ring i2 facilitate i centering of band I on the piston to provide uniform peripheral clearance at inside radial clearance space i5.

In a constructionwherein body i ofthe piston and securing ring I2 are of a metal, such as aluminum, having a greatercoetficient of expansion than band l, Figs. 5, 6 and '7 illustrate how band r 1 maybe made to have a loose axial fit with the piston cold and a tight-'fit at a predetermined higher operating temperature. Seating surfaces l and Il` are so inclined with respect to each other as to render angle X excessive or greater lo i.

stantially on axis A for obtaining the substan tially constantly tight uniform iit 'under all'tem- `perature conditions. As a result, the apex Y of the angle will be spaced from axis A and be a less distance from the periphery of the piston than the radial distance. Thus ifband 1 has a loose axial ilt with the piston at room temperature, as is illustrated in Fig. 5, it can be made to have a tight t at a predetermined higher operating temperature as is illustrated in Fig. 7, depending upon the distanceapex Y is from the axis A of the piston, which latter is a function of the extent to which the angle is rendered excessive. Ifbaud 1 were of a material having a higher coefficient of expansion thanl the remainder vof the piston, then if the angle X is rendered excessive, the reverse can be made to occur, namely, the band can be made to have a tight axial fit when the piston is cold and a loose axial t when the piston is hot. However, as was previously mentioned, a substantially constantly tight uniform nt may be obtainedl under all temperature conditions irrespective of the materials of band 1, piston body l, and securing ring I2, by having the apex Y of angle X substantially on the axis A of the piston.

In actual practice, it is desirable to have .the angle slightly excessive so thatv its apex Y is a slight distance from axis A and at a less distance from the periphery of the piston than the iradial distance, to compensate for any errors that may result from manufacturing tolerances and insure that at operating temperature of the piston the l. band will be held tight. In a piston wherein my.

invention is employedwhich is about four and one quarter (4.25) ,inches in diameter and the outside axial width of band 1 is about one-half (0.5) inch, thev angle X is rendered excessive `toy the extent ofY positioning apex Y about one onehundredth (0.01) of an inch from axis A, for the substantially on such axis.

has a lower coemcient oi' expansion than the remainder of the piston, can be made to have` a tight axial fit when cold and a loose axial ilt when hot. For this purpose, the angle' X formed by ,be a greater distance from the periphery-oi the piston than the radial distance. Thus, if band ll has a tight axial nt when the piston is cold, as is illustrated in Fig. 8, it will become looser axially as the piston becomes heated, as is illustrated in Fig. 10. The distancethe apex of angle X is from axis A, or in other words the extent to which l the angle is rendered insumcie'nt, will determine the temperature at which a proper tight fit may be obtained. If band `l were to have a higher coefllcient of expansion than the remainder of the piston, then the insuiilcient angle can -be made such as to provide the reverse, namely a loose axial t when cold and a tight axial fit when hot.

Although I ilnd my invention particularly applicable at. present in a piston having a periphs eral ring groove band, it is believed apparent from the preceding explanation, that the principle thereof is applicable in anyobject or body having an annular or ring like member to be mounted on or mounted in the periphery thereof; and this is so irrespective of whether such like member and the peripheralportion of thebody for mounting thereof form a true'circle. For example, such principle may be applied-to a. body hav:

' ing an irregular shape, and a band mounted in the periphery of such body and having-a peripheral shape corresponding to the peripheral shape of the portion of the body in which it is adapted for mounting. f

Aswas previouslymentioned, both of the seating surfaces of the band and the complementary seating surfaces of thev groove in which the band is mounted may be transversely inclined at an oblique angle with respect-to the axis A of the piston. Jig. i1 shows such arrangement with the apex Y of anglevX substantially on piston axis A, to provide a constantly tight uniform axial nt of band 2l in its seating groove under al1 temperature conditions. In the modification an inner peripheral iiange 2l on its top surface.

A relatively narrow flat ring 2l of resilient material, such as steel, is seated over band N in engagement with flange 2 8. Interposed between threadedsecuring ring Il -and ring Il is another Figs. 8, 9 and 10 illustrate howband l, whichy securing pins I3. Preferably, the underside of securing ring I2 is formed with a peripheral recess or channel I3' so as to avoid application of pressure directly over the outer peripheral portion of band. 1, and hence obviate pinching of a piston ring I4 which would result in undesirable distortion thereof. From the preceding it is seen that band 1 -is fitted or seated in a groove in the piston, between spaced apart surfaces and such ring groove being formed with blowby minimizing channel I1, more fully described, and claimed in my co-pending application Serial Number 344,305, filed July 8, 1940, entitled Piston construction. A projecting pin member I8 is fixed to compression ring I4 to clean out carbon from channel I1, as is also described more fully, and claimed in such application. Ring belt portion 6 of the piston also supports additional compression rings I9 and an oil ring 2|; blow-by minimizing channels 22 being also preferably formed in the upper sides of the ring grooves for compression rings I9. Although band 1 is shown with only one compression ring mounted thereon, it may be made axially wider to support a plurality of such rings if so desired.

The body I of the piston being preferably of a metal of relatively high heat conductivity, such as aluminum, has a greater coefficient, of expansion than band 1, which in order to provide a wear resistant seat for piston ring I4, is of harder metal, such as cast iron. Therefore, if such band 1 were mounted in a conventional form of seating groove having parallel seating surfaces extending transversely with respect to the piston axis A, and made to have a tight axial fit therein when the piston is at room or normal temperature, it would become axially loose as the piston heated up under working conditions, resulting in play with consequent misalinement and' loss of sealing eiliciency of piston ring I4. Furthermore, if band 1 were to have a greater coefllcient of expansion than the body of the piston, it would not have a uniform tight axial fit under all temperature conditions to which'the .piston might be subjected,

which would also resultin misalinement of the piston ring therein. Even if band 1 were of the same material as that of body I of the piston, play or distortion thereof might very readily occur under varying temperature conditions, because the band being at the periphery ofthe piston in contact with the cylinder wall under operating conditions and temperatures, is maintained cooler than the interior of the piston body, and would, therefore, expand and contract to a different-degree Furthermore, such peripheral band is adjacent the crown of the piston, the central portion of' which is hotter under operating conditions than the periphery of the piston. Consequently, this also causes the band to be cooler, so as to expand or` contract to a difere'nt degree.

I'have found -that predetermined control of the axial fit of -band 1 in the piston under varying temperature conditions, can be obtained by in.

clination of the groove seating surfaces 8 and Il with respect to each other and bysimilar inclination of the complementary seating surfaces on band 1, to form an angle X, the apex Y of which has a predetermined relationship with respect to the axis A of the piston. In this connection, it should be kept in mind that the body of the piston being substantially cylindrically shapedwill expand or contract uniformly with respect to axis A as a locus when all portions thereof are subjected to the same temperature changes; and the various figures formed during such expansion or contraction will al1 be similar to the shape of the piston body at room or normal temperature. Band 1, being circular and being substantially concentric with respect to the axis A will also expand or contract uniformly with respect to such axis A when subjected to the same temperature changes. Hence, if angle X, irrespective of shape or size, is such that its apex Y 'lies substantially on axis A, then band 1 will always have a substantially` constantlyltlght uniform axial flt between seating surfaces 8 and II; irrespective of whether the piston .is hot or cold. This is true irrespective of the materials of band 1, piston body I, and securing ring I2. i

With respect to my preferred form of piston construction illustrated in Figs. l and 2, angle X is shown such that its apex Y lies substantially on axis A to maintain the described constantly tight uniform axial fit under all varying temperatures to which the piston may be subjected. However, in the actual piston manufactured by my assignee, such angle apex is spaced a slight distance from the axis (but may be considered substantially thereon) for a reason to be subsequently explained. Figs'. 3 and 4 illustrate graphically how such fit remains substantially constant during temperature changes. Fig. 3 depicts the piston at room temperature but exaggerates the relationship of band 1 in its seating groove; while Fig. 4 illustrates the piston expanded by heat to substantially operating temperature, the size thereof compared to Fig. 3 being exaggerated but the parts thereof being shown in substantially proper relationship. From these views, it can be seen that although there is transverse displacement of band 1 with' respect to the body of the piston duringexpansion or contraction, nevertheless a substantially constantly tight uniform flt of band 1 between seating surfaces B and II will always obtain. `In this connection, as was previously explained, body I of the piston. being preferably of aluminum, has a greater coefficient of expansion than band 1 which is preferably of cast iron. Consequently, as can be observed from comparison of Figs. 3 and 4, the inside radial clearance space I5 between band 1 and body I becomes less as expansion of the parts occurs by heat.- It is for this reason that the radial clearance space I5 is provided, because if band 1 were to ttight radially against the piston body when the parts are vat room temperature, then when the parts expanded to their size under substantially operating temperature of the piston, the t would be too tight causing undesirable distortion which my invention is designed to obviate. Therefore, clearance space IB is such that when the parts are at room temperature, sufficient space still remains when the parts have expanded to their size at substan- 'tially operating temperature, to preclude radial ring 32 having an outer peripheral flange 3l on its underside in engagement with ring 2l. Because of the resilient character of ring and the opposed relationship of flanges 28 and Il, band 2l is resiliently thrust against seatingshoulder 21. As expansion or contraction occurs in an axial direction, resulting .from changes in temperature. the resilient means, including ring 29,.

will yield to permit such changes, but at the same time will always maintain band 2i with a tight flt in its sea'ting'groove, to thereby maintain proper alinement of piston ring seated in the band. If desired ring 32, may be omitted, and flange 33 formed directly on securing ring 3i which may be made axially wider for this pur- Pose. The modification of Figs. 12 and 13 is not as desirable as the preferred form of the invention illustrated in Figs. 1 and 2, because the latter construction is more durable and simple, and more economical to manufacture.

I claim:

1. A piston having in-the periphery thereof an aniilar member seated between lsurfaces inclined wit respect to each other to form anangle the apex of which is spaced a predetermined distance oi! the axis of said piston for providing a predetermined loose or tight fit of said member at a predetermined temperature within a varying temperature range.

2. A body having a locus from whichexpansion and contraction occurs resulting from changes in temperature and having in the periphery thereof a member seated between surfaces in 4 clined with respect to each other `to forml an angle the apex of which is spaceda predetermined distance oif said locus for providing a predetermined loose or tight ilt of said member attransverses with respect to che exis of seid pieton, and ananular member seated in said groovev and having complementary spaced apart seating surfaces engaging said groove seating surfaces;. said surfaces engaging invplanes inclined with respect to eachother to form an angle the apex of which although substantially on said piston axis to provide a uniform fit of said member in said groove `under varying temperature conditions, is spaced a slight distance from said axis and at a distance from the periphery ofthe piston less than the radial distance to insure a tight iit at `operating temperatures of the piston.

6. The method of providing a predetermined loose or tight fit at a predetermined temperature between a body having a locus from which a predetermined temperature within a varying temperature range.

3. A piston provided with a peripheral groove having spaced apart seating surfaces extending transversely with respect to the axis of said piston, and an annular member seated in said groove and having complementary spaced apart seating surfaces engaging said groove seating surfaces, said surfaces engaging in planes inclined with respect to each other to form an angle the apex of which is spaced a predetermined distance od said piston axis for providing a predetermined loose or tight t between said groove and said member at a predetermined temperature within a varying temperature range'as said groove and said member expand or contract.

4. A piston comprising a body having a peripheral recess adjacent the crown thereof and which forms a peripheral shoulder having a seating surface, a piston ringgroove band having a seating surface engaging said shoulder seating surface `and also an opposite seating surface. and a securing ring insaid recess over said band and `having a seating surface engaging said oppositeI seating surface of said band; said shoulderseating :surface and said band seating surface in engagement therewith lying in a plane at substantially a right angle with respect to the axis of said tially tight fit of said bandl between said shoulder and said securing ring under varying temperature conditions.

5. A piston provided with a peripheral groove having spaced apart seating surfaces extending seating surface in engagement thereexpansion and contraction occurs resulting from changes in temperature and a member adapted to be seated between siufaces in said body and having a dinerent coeillcient of expansion than that of the body. which comprises providing inclination of such surfaces with respect to each other to form anangle, and locating the apex of said angle in such spaced relationship with respect to said locus as to' determine said fit at said predetermined temperature.

7. A piston comprising a body of Valuminum having al peripheral recess adiac'ent the crown thereof which forms a peripheral 'shoulder having a' seating surface extending at substantially a rightangle with respect to the axis of said piston, an iron piston ring groove band for providing a wear-resistant,l seat for a piston ring and having a seating surface engaging said shoulder yseating surface so as to extend also at substanlsaid band; said securing ring surface and said opposite surface of said band being inclined with respect to said shoulder seating surface to form an angle the apex of which lies substantiallyon said piston axis to provide a substantially tight uniform iit of said band between said shoulder and said securing ring under varying temperature conditions.

8. A piston comprising a' body of aluminum having a peripheral recess adjacent the crown thereof which forms a peripheral shoulder having a seating surface extending at substantially a right angle with respect to the axis of said piston,l an iron piston ring groove band for providing a wear-resistant seat for a piston ring and having a seating surface engaging said shoulder seating surface so as to extend also at substantially a right angle with respect to the axis of said piston, said band being free of molecular union with said body and having also an opposite seating surface, and a securing ring in said vrecess over `said band and having a seating surt of said band at operating temperatures off the piston. f

9. A piston comprising a body of' relatively soft metal such as aluminum or the like, the body having a peripheral 'recess adiacent thev crown shoulder against rotational movement about the` axis of the piston andhavin'g a seating face engaging said opposite face of the band; said :faces engaging along surfaces inclined with respect to each other, and the straight line generatrices of said surfaces forming'an angle the apex of which has a predetermined relationship with respect to the axis of the piston for providing a predetermined fit of said band between said shoulder 'and said securing ring ata predetermined temperature within a varying temperature range; the contact between said shoulder seating face and said Al'aand'seating face in engagement therewith being in a plane at substantialiya right angle with respect to the axis of said piston, to enhance centering of the band and alinement with respect to a cylinder wall of a piston ring seated in the/groove of the hand. i Y

10. 'A piston comprising a body of relatively soft metal such as aluminum or the like, the body having a peripheral recess adjacent the crown thereof which orns a peripheral shoulder band againstl the body' and hence preclude distortion; said faces engaging along surfaces inclined with respect to each other, and the straight line generatrices of said surfaces forming an angle the apex of which is spaced od of the axisvof the piston a predetermined distance from the periphery of said piston less than the radial distance to provide a tight fit of said band between said shoulder and said securing ring at operating temperatures of thepiston.

1i. a .piston comprising a body of relatively( soft metal suchas aluminum or-the like, the body having a peripheral recess adjacent the crown thereof which forms a peripheral shoulder having a seating face, an unbroken peripherally grooved piston ring groove band of harder material than the body to provide a wear resistant seat for 'a piston ring adapted to be seated in its groove, said band being free of molecular union with said body and having a seating face engaging said shoulder seating face and also an opposite face, and a securing ring in the recess over' vsaid band rmly clamping the band on the shoulder against rotational movement about the ams having a seating face, an unbroken peripherally grooved piston ring groove band of harder material than the body to provide a wear resistant seat for a piston ring adapted to be seated in its groove, said band being free of molecular union with said body and having a seating face engaging said shoulder seating face and also an opposite face, Iand a securing ring in the recess over said .band rmly clamping the band on the, shoulder againstmotational movement about the axis of the piston and having a seating face 'engaging said 'opposite face of the band, the band iitting with inside radial clearance with respect to the piston body to preclude radial binding of the of the piston' and having a seating face engagp. ing said opposite face of the band, the `part of said securing ring adjacent the band having a peripheral recess t'opreclude application o direct pressure to the outer peripheral portion of said band and hence obviate lpinching of the piston ring and said band fitting with inside radial clearance with respect to the piston body to pre-Y clude radial binding of the band against the body and hence preclude distortion; said faces engaging along surfaces inclined with respect to each other, and the straight line generatrlces oi said surfaces forming an angle the apex of which has a predetermined relationship with respectrto the axis of the piston for providing a predetermined fit of said band between said shoulder and said securing ring at a predetermined` temperature within a varying temperature range; the

contact between said shoulder seating face and said band seating face in engagement therewith being in a plane at substantially a right angle with respect to the axis of said piston, to enhance centering ofthe band and alinement with'respect to a cylinder wall of a piston ring seated inthe groove of the band.

OSCAR L. STARR. 

